Vibration-isolating and impact-absorbing case comprising vibration-damping footing

ABSTRACT

According to certain embodiments, a vibration-isolating case comprises a resilient, plastic-composite walled case and vibration-damping footing located at the bottom side of the case. Each vibration-damping footing comprises a mounting plate, cushions, and a damping system. The mounting plate has a flat surface and side surfaces extending from the flat surface to form a channel-shaped structure. The flat surface is positioned proximate a bottom outer surface of the case and couples to at least one brace within the case. The cushions are positioned within the channel-shaped structure such that the side surfaces of the mounting plate protect at least a top portion of each cushion. The damping system is positioned between the cushions and comprises a tray containing a quantity of inelastic particulate. A mechanical path exists between the vibration-damping footing and a platform mounted within the case.

RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No.62/201,057, filed Aug. 4, 2015 and entitled “Reusable Component Systemfor Transporting and Storing Fragile Objects,” and U.S. ProvisionalApplication No. 62/315,221, filed Mar. 30, 2016 and entitled “ModularSystem for Transporting Fragile Objects.”

TECHNICAL FIELD

Certain embodiments of the present disclosure relate, in general, totransporting and storing fragile objects and, more particularly, to anisolation system for transporting and storing fragile objects.

BACKGROUND

Fragile objects may be at risk of becoming damaged when transported fromone location to another. To minimize the risks, fragile objects aretraditionally transported in wooden crates. The wooden crates arecushioned with foam intended to protect the fragile object in the eventthat the wooden crate is dropped.

SUMMARY

Embodiments of the present disclosure may reduce the risk of a fragileobject becoming damaged during transit. For example, disclosed herein isa vibration-isolating system comprising a case, one or moreenvironmental buffers, a platform suspended within the case by aplurality of wire rope isolators, a crumple zone beneath the platformand configured with one or more shock-absorbing structures (such asshock-absorbing structures that comprise polycarbonate, polypropylene,and/or expanded polystyrene), and a container assembly configured on theplatform. The container assembly is operable to protect a payload. Thepayload comprises a flexible panel, such as a painting painted on astretched canvas, a substantially flat membrane, or any other object forwhich vibration can cause acute or accumulated deterioration. Thecontainer assembly comprises a back panel positioned behind the flexiblepanel and offset by a first substantially airtight compartment, a frontpanel positioned in front of the flexible panel and offset by a secondsubstantially airtight compartment, and a stiffener panel positioned infront of the front panel and offset by a third substantially airtightcompartment.

In certain embodiments, the wire rope isolators are tuned to yield atuning ratio greater than or equal to 1.4, the tuning ratio determinedby dividing a natural frequency of the flexible panel within thecontainer assembly by a natural frequency of the vibration-isolatingsystem. For example, tuning the wire rope isolators comprises selectingat least one of the following characteristics based at least in part onthe weight of the container assembly: wire thickness, number of wires ina rope braid, number of loops in the wire rope isolator, loop diameter,loop spacing, number of wire rope isolators, angle of orientation ofwire rope isolators relative to the platform, and/or position of thewire rope isolators relative to the platform.

In certain embodiments, the vibration-isolating system further comprisesone or more vibration-damping footings. The vibration-damping footingsare coupled proximate an outer bottom surface of the case. Eachvibration-damping footing comprises a mounting plate, a first cushionand a second cushion coupled to a bottom side of the mounting plate, anda damping system positioned between the first cushion and the secondcushion. The damping system comprises a tray containing a quantity ofinelastic particulate. Mechanical continuity exists between the one ormore vibration-damping footings outside the case and the platform withinthe case.

In certain embodiments, the container assembly is tuned to reduce theextent to which the flexible panel experiences excursions greater than350 microns. For example, the front panel, the back, panel, and thestiffener panel each comprise one or more rigid materials, each rigidmaterial having higher natural frequency and lower excursion propertiesthan the less rigid flexible panel, and the container assembly is tunedusing fixed, gas-piston principles to impart the higher naturalfrequency and lower excursion properties of the rigid materials to theflexible panel such that the extent to which the flexible panelexperiences excursions greater than 350 microns is reduced. Certainembodiments may eliminate excursions greater than 350 microns.

In certain embodiments, the front panel of the container assemblycomprises an acrylic offset from the flexible panel by an air gap havinga depth of approximately 3-10 millimeters, and the stiffener panel ofthe container assembly comprises a paper honeycomb sheet offset from thefront panel by an air gap having a depth of approximately 3-5millimeters.

In certain embodiments, the environmental buffers comprise silica geltiles and/or thermal phase change tiles positioned within the case, andmicroclimate control within the back panel of the container assembly. Asan example, the microclimate control within the back panel comprises aback board comprising a foam core board having thermal insulationproperties and a vapor-proof seal, a humidity control layer comprising asilica gel felt positioned between the flexible panel and the backboard, and zeolite clay and/or activated charcoal embedded paper boardsoperable to absorb volatile organic compounds (VOCs) emitted by theflexible panel.

Also disclosed is a vibration-isolating system comprising a platformsuspended in a vertical orientation relative to ground. The platform issuspended by a plurality of wire rope isolators. Each wire rope isolatorcomprises a wire braid arranged into one or more loops and at least onebracket configured to hold the one or more loops in place. At least oneof the wire rope isolators is positioned proximate a top side of theplatform and at least one of the wire rope isolators is positionedproximate a bottom side of the platform.

In certain embodiments, the wire rope isolators are tuned to yield atuning ratio greater than or equal to 1.4, the tuning ratio determinedby dividing a natural frequency of an object that thevibration-isolating system protects by a natural frequency of thevibration-isolating system. For example, tuning the wire rope isolatorscomprises selecting at least one of the following characteristics basedat least in part on the weight of the load: wire thickness, number ofwires in a rope braid, number of loops in the wire rope isolator, loopdiameter, loop spacing, number of wire rope isolators, angle oforientation of wire rope isolators relative to the platform, and/orposition of the wire rope isolators relative to the platform.

In certain embodiments, the wire rope isolator(s) positioned proximatethe bottom side of the platform are supported by one or morechevron-shaped structures. In certain embodiments, the plurality of wirerope isolators comprises a first pair of wire rope isolators coupledproximate the top side of the platform toward the left, a second pair ofwire rope isolators coupled proximate the top side of the platformtoward the right, a third pair of wire rope isolators coupled proximatethe bottom side of the platform toward the left, and a fourth pair ofwire rope isolators coupled proximate the bottom side of the platformtoward the right. Each pair of wire rope isolators comprises one wirerope isolator that generally faces toward the front surface of theplatform and one wire rope isolator that generally faces toward the backsurface of the platform. The system can also include at least one wirerope isolator coupled proximate the right side of the platform towardthe middle of the right side and at least one wire rope isolator coupledproximate the left side of the platform toward the middle of the leftside.

In certain embodiments, the platform comprises a first shelf portionextending from the front side of the platform and a second shelf portionextending from the back side of the platform, each shelf portionoperable to carry a load.

In certain embodiments, wire rope isolator(s) positioned proximate thebottom side of the platform have a different wire thickness, number ofwires in a rope braid, number of loops in the wire rope isolator, and/orloop diameter than wire rope isolator(s) positioned proximate the topside of the platform.

In certain embodiments, at least one of the wire rope isolatorscomprises a first bracket coupled to the platform and a second bracketcoupled to a brace operable to mount the platform within a case. Certainembodiments position an impact-responsive, variable stiffness foamstructure through a space formed by the loops of said at least one ofthe wire rope isolators such that the foam structure is an impactattenuation material between the first bracket and the second bracket.The system can further include a vibration-damping footing outside thecase. The vibration-damping footing comprises a mounting plate and atleast one cushion coupled to the mounting plate. Mechanical continuityexists between the vibration-damping footing and the platform via thebrace and the at least one wire rope isolator coupled to the brace.

In certain embodiments, the platform comprises a thermal phase changematerial encased within one or more aluminum honeycomb panels.

Also disclosed is a vibration-isolating system for protecting an objectduring transit. The vibration-isolating system comprises a platform anda container assembly configured on the platform. The container assemblycomprises a back panel positioned behind the object and offset by afirst substantially airtight compartment, a front panel positioned infront of the stretched canvas and offset by a second substantiallyairtight compartment, and a stiffener panel positioned in front of thefront panel and offset by a third substantially airtight compartment.The front panel, the back, panel, and the stiffener panel each compriseone or more rigid materials, each rigid material having higher naturalfrequency and lower excursion properties than the less rigid object. Thecontainer assembly is tuned using fixed, gas-piston principles to impartthe higher natural frequency and lower excursion properties of the rigidmaterials to the object such that the extent to which the objectexperiences excursions greater than 350 microns is reduced. A pluralityof isolators suspend the platform in a vertical orientation relative toground and are tuned to yield a tuning ratio greater than or equal to1.4, the tuning ratio determined by dividing a natural frequency of theobject that the vibration-isolating system protects by a naturalfrequency of the vibration-isolating system.

Also disclosed is a vibration-isolating case comprising a case, a firstvibration-damping footing located at the bottom side of the case andtoward the left, and a second vibration-damping footing located at thebottom side of the case and toward the right. The case is a resilient,plastic-composite walled case. Each vibration-damping footing comprisesa mounting plate, first and second cushions, and a damping system. Themounting plate comprises a flat surface and side surfaces extending fromthe flat surface to form a channel-shaped structure. The mounting plateis coupled to the case such that the flat surface is positionedproximate a bottom outer surface of the case with the channel-shapedstructure facing away from the case and extending in the front-to-backdirection of the case. The flat surface couples to at least one bracewithin the case (the at least one brace is positioned proximate a bottominner surface of the case). The first and second cushions are positionedwithin the channel-shaped structure such that the first cushion islocated toward the front of the case and the second cushion is locatedtoward the back of the case. The side surfaces of the mounting plateprotect at least a top portion of each cushion. The damping systemcomprises a tray positioned between the first cushion and the secondcushion. The tray contains a quantity of inelastic particulate. Theplatform is mounted within the case such that a mechanical path existsbetween the platform, the at least one brace, and the first and secondvibration-damping footing.

Also disclosed is a vibration-damping footing. The vibration-dampingfooting comprises a mounting plate, a damping system coupled to themounting plate, and at least one cushion coupled to a bottom side of themounting plate. In certain embodiments, the mounting plate furthercomprises side portions adjacent to the cushion and operable to protectthe cushion. In certain embodiments, the damping system comprises atray. The tray can contain a quantity of inelastic particulate, such aslead shot. In certain embodiments, the depth of the tray, the diameterof the inelastic particulate, and/or the amount of inelastic particulatein the tray is selected to optimize damping performance. In certainembodiments, the inelastic particulate is suspended in a gel.Alternatively, the inelastic particulate may be surrounded by air. Incertain embodiments, the cushion is an air cushion comprising anair-release hole diameter selected to optimize damping performance.

In certain embodiments, the mounting plate comprises a flat surface andside surfaces extending from the flat surface to form a channel-shapedstructure, the at least one cushion comprises a first air cushion and asecond air cushion positioned within the channel-shaped structure suchthat the side surfaces of the mounting plate protect at least a topportion of each air cushion, and the damping system is positionedbetween the first air cushion and the second air cushion. The dampingsystem comprises a tray containing a quantity of inelastic particulate.

Also disclosed is a vibration-isolating case comprising a case and atleast one vibration-damping footing coupled to a bottom side of thecase. Examples of the vibration-damping footing were described in theprevious paragraphs.

Also disclosed is a container assembly for protecting a flexible panel,such as a stretched canvas or other flexible membrane or panelstructure. The container assembly comprises a back panel, a front panel,and a stiffener panel. The back panel is positioned behind the flexiblepanel and offset by a first substantially airtight compartment. The backpanel comprises a back board, a decontamination layer, and a humiditycontrol layer. The decontamination layer and the humidity control layerare positioned between the flexible panel and the back board. The frontpanel comprises an acrylic material. The front panel is positioned infront of the flexible panel and offset by a first gasket resulting in asecond substantially airtight compartment. The second substantiallyairtight compartment has a depth in the range of 3-10 millimeters. Thestiffener panel is positioned in front of the front panel. The stiffenerpanel is offset by a second gasket resulting in a third substantiallyairtight compartment. The third substantially airtight compartment has adepth in the range of 3-5 millimeters. A frame surrounds the peripheryof the flexible panel. A third gasket seals between the back panel andthe frame, a fourth gasket seals between the flexible panel and theframe, and a fifth gasket seals between the front panel and the frame.The front panel, the back, panel, and the stiffener panel each compriseone or more rigid material. Each rigid material has higher naturalfrequency and lower excursion properties than the flexible panel. Thecontainer assembly is tuned using fixed, gas-piston principles to impartthe higher natural frequency and lower excursion properties of the rigidmaterials to the flexible panel such that the natural frequency of theflexible panel increases and the extent to which the flexible panelexperiences excursions greater than 350 microns is reduced.

Also disclosed is a container assembly comprising a back panel and afront panel. The container assembly may be configured to protect asubstantially flat object. The back panel is positioned behind theobject and offset by a first sealed air compartment. The front panel ispositioned in front of the object and offset by a second sealed aircompartment. In certain embodiments, the second sealed air compartmentis dimensioned so as to tune the natural frequency of the object againstvibrations. For example, the offset of the second sealed air compartmentis dimensioned so that the object and the front panel are in closeproximity. In certain embodiments, each of the first and second sealedair compartments is substantially airtight. In certain embodiments, theobject comprises a stretched canvas within a frame and the containerassembly further comprises a first gasket between the back panel and theframe, a second gasket between the object and the front panel, and athird gasket between the front panel and the frame.

Also disclosed is a container assembly comprising a back panel, a frontpanel, and a stiffener panel. The container assembly may be configuredto protect a substantially flat object. The back panel is positionedbehind the object and offset by a first sealed air compartment. Thefront panel is positioned in front of the object and offset by a secondsealed air compartment. The stiffener panel is positioned in front ofthe front panel and offset by a third sealed air compartment.

In certain embodiments, the offset between the object and the frontpanel is within the range of approximately 3-10 millimeters and theoffset between the front panel and the stiffener panel is within therange of approximately 3-5 millimeters. In certain embodiments, thefront panel comprises an acrylic material, the stiffener panel comprisesa paper honeycomb sheet, and/or the back panel comprises a foam coreboard. The back panel can further comprise a decontamination layer and ahumidity control layer positioned between the foam core board and theobject.

In certain embodiments, the container assembly further comprises a firstgasket positioned between the object and the front panel and a secondgasket positioned between the front panel and the stiffener panel. Thegasket positioned between the front panel and the stiffener panel canhave a non-rectangular geometry. The stiffener panel can have anon-uniform thickness such that a volume of a corner portion of thethird sealed air compartment is reduced as compared to the volume of amiddle portion of the third sealed air compartment.

In certain embodiments, the object has a natural frequency in the rangeof 1 Hz to 20 Hz and the first sealed air compartment is dimensioned soas to increase the natural frequency of the object by at least 20%, thesecond sealed air compartment is dimensioned so as to increase thenatural frequency of the object by at least 20%, and the third sealedair compartment is dimensioned so as to increase the natural frequencyof the object by at least 20%. In certain embodiments, the combinationof the first, second, and third sealed air compartments increase thenatural frequency of the object to at least 40 Hertz.

In certain embodiments, each of the first, second, and third sealed aircompartments are substantially airtight.

Certain embodiments of the present disclosure may provide one or moretechnical advantages. Certain embodiments may protect a canvas painting,art, or other fragile object from vibration and/or shock that can occurduring transit. As an example, certain embodiments may provide avibration-isolating case that dampens vibrations and/or shockexperienced by the object in transit. The case can be configured toisolate damaging frequencies and/or to absorb shock in the event thatthe case is dropped. As another example, certain embodiments may raisethe natural frequency of the object. For example, the object may bearranged within a panel system that raises the natural frequency of theobject well above its fundamental damage frequency. Raising the naturalfrequency may prevent resonance that would otherwise amplify vibrationsacross the object. Certain embodiments may tune or customize protectionbased on the particular object being transported, for example, dependingon the fundamental damage frequency of the object. Certain embodimentsmay have all, some, or none of these advantages. Other advantages willbe apparent to persons of ordinary skill in the art.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates an example of a suspension system for transportingand storing a load, in accordance with certain embodiments of thepresent disclosure.

FIG. 2 illustrates an example of a vibration-isolating case, inaccordance with certain embodiments of the present disclosure.

FIG. 3 illustrates another example of vibration-isolating case, inaccordance with certain embodiments of the present disclosure.

FIGS. 4A-4B illustrate examples of wire rope isolators for a suspensionsystem, in accordance with certain embodiments of the presentdisclosure.

FIG. 5 illustrates an example of a vibration-damping footing, inaccordance with certain embodiments of the present disclosure.

FIG. 6 illustrates an example of a vibration-damping footing, inaccordance with certain embodiments of the present disclosure.

FIG. 7 illustrates an example container assembly for a load, inaccordance with certain embodiments of the present disclosure.

FIG. 8 illustrates an example container assembly for a load, inaccordance with certain embodiments of the present disclosure.

DETAILED DESCRIPTION

Fragile objects are traditionally transported in wooden crates cushionedwith foam. The foam is intended to protect the fragile object in theevent that the wooden crate is dropped. Traditional wooden crates,however, may fail to adequately protect the fragile object from damage.For example, the fragile object may be subjected to significantvibrations when transported by a truck, aircraft, or other vehicle. Thevibrations stress the fragile object and may result in cracks or otherdamage. As an example, the fragile object may be a painting on a canvas.As the paint ages, it tends to become less flexible and more brittle.When vibrations occur, the canvas takes the vibration and the paintrestrains the canvas thereby absorbing the kinetic energy of the canvas.If the absorbed energy exceeds stress limits, the paint will crack andseparate either at the point of adhesion of the paint to the canvas orbetween paint layers. Essentially the paint layers start to transformfrom a continuous film to a series of fragmented sections. Every time acrack forms, that crack becomes the focal point of movement in thatarea. As more movement occurs, the paint gets more and more damaged atthe cracks.

The most damaging vibrations generally occur at frequencies similar tothe object's natural frequency. At the object's natural frequency,resonance occurs that amplifies movement. The natural frequency of apainting will generally be in the range of approximately 5-20 Hz and thenatural frequency of a glass sculpture or ceramic will generally be inthe range of approximately 50-150 Hz. In developing the systems andmethods disclosed herein, it was discovered that traditional woodencrates not only fail to reduce damaging vibrations, they actually makethe vibrations worse. For example, testing was performed on atraditional wooden crate configured with accelerometers placed inside apainting, inside the foam cushioning, outside the wooden crate, and onthe bed of the truck transporting the painting. The testing demonstratedthat traditional foam has a relatively low natural frequency(approximately 20-40 Hz) and therefore amplifies vibrations in damaginglow frequency ranges. At every point in which foam was added, vibrationacross the painting increased. That is, the displacement energyexperienced by a painting cushioned in foam was worse than if thepainting had been placed directly on the bed of the truck. By amplifyingthe displacement energy, the foam increased the risk of damage to thepainting.

The results obtained by testing the foam were unexpected becauseconventionally foam was thought to be beneficial for protecting fragileobjects and because foam behaves differently when observed on its own ascompared to when it is observed carrying a load. Both in productliterature and in experimental tests on engineering shaker tables andactual road tests, cushioning foams made from open-cell polyurethane(PEU) and extruded, closed-cell polyethylene foams exhibit consistentnatural frequencies between 3 Hz-35 Hz, depending upon theconfigurations used as container cushions and the payload compressionscreated. These are precisely the frequencies transmitted in all modes ofmotor, rail and air freight transportation. Because the input forcefrequencies equal the natural frequencies of the foam cushions, theamplitudes of the vibrations experienced are amplified. Embodiments ofthe current system seek to resolve this problem by creating componentswhich can predictably raise the natural frequency of the payload withoutmechanical contact and by tuning the suspension system to affectcritical damping of input vibration energies.

Certain embodiments of the present disclosure may provide solutions tothis and other problems associated with traditional systems fortransporting fragile objects. For example, certain embodiments mayreduce exposure to vibration frequencies that would otherwise damage afragile object in transit, such as vibrations in lower frequency ranges(e.g., vibrations less than approximately 150 Hz, vibrations less thanapproximately 100 Hz, or other frequencies depending on the naturalfrequency of the object being transported). Certain embodiments use asuspension system to provide tunable protection from vibration andshock. The suspension system includes a platform to carry the object.The platform connects to isolators that suspend the platform. Theisolators may be tunable to dampen vibrations occurring at the naturalfrequency and/or raise the natural frequency of the load to a frequencysufficiently above the fundamental damage frequency of the object.

In certain embodiments, the suspension system may be packed inside avibration-isolating case. The vibration-isolating case may include asturdy case and vibration-damping footing. The vibration-damping footingmay be tuned to dampen certain damaging frequencies, such aslow-frequency, large displacement frequencies, for example, frequenciesless than approximately 5 Hz. In addition, if the fragile object issubstantially flat, the fragile object may be packaged using a panelsystem, for example, prior to being loaded onto the platform of thesuspension system and/or being packed inside the vibration-isolatingcase. The panel system provides protection during transit by controllingmotion across the fragile object. In general, the panel system placesthe substantially flat object, such as a painting, between panels on thefront and back sides of the object. Substantially airtight air gapsbetween the flat object and the panels increase stiffness that reducesvibration movement across the flat object. Additional panels may be usedto increase stiffness.

For a more complete understanding of the present invention and theadvantages thereof, reference is now made to the following descriptionand the accompanying drawings, wherein like numerals are used for likeand corresponding parts of the various drawings.

FIG. 1 illustrates an example of a suspension system 100 fortransporting and storing a load, in accordance with certain embodimentsof the present disclosure. Suspension system 100 may include a platform110 configured to carry a load 120. For purposes of explanation, FIG. 1illustrates the orientation of suspension system 100 relative to anx-axis extending in the direction of platform 110's length (e.g., fromleft to right), a y-axis extending in the direction of platform 110'sheight (e.g., from top to bottom), and a z-axis extending in thedirection of platform 110's width (e.g., from front to back). In theexample illustrated in FIG. 1, platform 110 provides a flat surface tosupport load 120 in an x-y plane. Platform 110 optionally includes ashelf 115, such as a flange that projects outward in the x-z plane tofurther support load 120. Platform 110 may comprise any suitablematerial, such as metal, plastic, wood, cardboard, etc. In certainpreferred embodiments, platform 110 comprises rigid material having ahigh natural frequency, for example, platform 110 comprises one or morelight-weight aluminum honeycomb panels.

Load 120 includes an object 300, such as a painting, drawing, sculpture,artifact, museum specimen, or other fragile object. In some embodiments,the load may further include packaging. For example, object 300 may bepackaged within a container assembly, such as the panel system describedwith respect to FIGS. 7-8 below. The panel system (or object 300 itselfin embodiments that do not use a panel system) can optionally beenclosed within a box or other protective covering, such as aweatherproof (or rain proof) cover comprising stretch wrap, polyfilm,KEVLAR®, life raft material, vinyl, thermal blanket, and/or othersuitable material. Load 120 may be secured to platform 110 using one ormore latches and/or other securing mechanisms. In certain embodiments,platform 110 may carry more than one load. As an example, multiple loads120 could be carried on the same surface of platform 110 (not shown). Asanother example, FIG. 1 illustrates a first load 120 a on a firstsurface of platform 110 and a second load 120 b on the opposite surfaceof platform 110. To carry loads on opposite surfaces, platform 110 mayinclude a first shelf portion extending from the front side of theplatform and a second shelf portion extending from the back side of theplatform. The first and second shelf portions can be separate shelves,or they can be a single shelf that wraps around platform 110 or isbisected by platform 110.

Suspension system 100 further includes isolators 130 configured tosuspend platform 110. In general, isolators 130 reduce movement ofplatform 110 carrying load 120. As an example, isolators 130 may reducevibrations that can occur when transporting platform 110 by truck,aircraft, or other vehicle. As another example, if suspension system 100is dropped, isolators 130 may dampen the impact on platform 110. Anysuitable isolators may be used. Examples of isolators 130 include wirerope isolators, rubber air bladders, inflatables, smartfoam, or otherstructures operable to suspend platform 110. Examples of wire ropeisolators are further described with respect to FIGS. 4A-4B below.Various embodiments may comprise one type of isolator 130 (e.g., wirerope isolators only) or multiple types of isolators (e.g., wire ropeisolators and smartfoam isolators).

Isolators 130 may be placed in any suitable location, such as at the topof platform 110, at the bottom of platform 110, and/or at the sides ofplatform 110. FIG. 1 illustrates an example that includes six points ofisolation in the following general locations: top-left (isolators 130a), top-right (isolators 130 b), bottom-left (isolators 130 c),bottom-right (isolators 130 d), left-middle (isolator 130 e), and rightmiddle (isolator 1300. Each point of isolation may include one or moreisolators 130. In the embodiment shown in FIG. 1, isolators 130 a, 130b, 130 c, and 130 d comprise two isolators each, wherein each pair ofisolators 130 comprises one isolator that generally faces toward thefront surface of platform 110 and one isolator that generally facestoward the back surface of platform 110, and isolators 130 e and 130 fcomprise one isolator each for a total of ten isolators. As illustratedin FIG. 1, isolators 130 are configured such that platform 110 isoriented in a substantially vertical direction relative to the ground.

In certain embodiments, suspension system 100 includes one or morebraces 140 to facilitate mounting platform 110 within a container, suchas a vibration-isolating case 200 described with respect to FIGS. 2-3below. Brace(s) 140 may have any suitable configuration. As an example,FIG. 1 illustrates four braces 140, and each brace 140 comprises a rigidplate configured to couple one or more isolators 130 to an inner wall ofthe container. In the example, brace 140 a couples to isolators 130 a(top left), brace 140 b couples to isolators 130 b (top right), brace140 c couples to isolators 130 c (bottom left), and brace 140 d couplesto isolators 130 d (bottom right). As another example, in an alternativeembodiment, brace 140 may comprise a frame within the container, asshown in FIG. 3. Although FIG. 1 illustrates a certain arrangement ofload 120, isolators 130, and braces 140, other embodiments may use anysuitable number and arrangement of these components.

In certain embodiments, suspension system 100 may be configured within avibration-isolating case. FIG. 2 illustrates an example of avibration-isolating case 200, in accordance with certain embodiments ofthe present disclosure. Vibration-isolating case 200 comprises case 205and vibration-damping footing 210. Case 205 may be any case suitable tocontain suspension system 100. Case 205 may be a commercial casemanufactured by PELICAN™, STORM CASE™, FAWIC™, or some othermanufacturer. Alternatively, case 205 may be a custom case manufacturedspecifically for vibration isolation. Case 205 may be made of metal,plastic, rubber, and/or other suitable material. The design of case 205may provide protection from the elements (e.g., moisture, heat, dust,etc.). In certain preferred embodiments, case 205 is a resilient,plastic-composite walled case that is weather-proof, water-proof,acoustically-sealed, resilient (e.g., able to retain its shape after animpact), shock-absorbing, and puncture-resistant, such as apolypropylene honeycomb sandwich panel-walled FAWIC™ case with aluminumextrusion corners and seams or a roto-molded polyethylene PELICAN™ case.

Case 205 may comprise front, back, left, right, top, and bottom sides.The bottom side of case 205 may be positioned to take the gravitationalload during transit, and the top side of case 205 may be positionedopposite the bottom side. For purposes of explanation, the front andback sides of case 205 may extend along the length of the object beingtransported, as depicted by the x-axis in FIG. 1, and the left and rightsides may extend along the width of the object being transported, asdepicted by the z-axis in FIG. 1.

Case 205 may comprise one or more doors 202 for accessing the interiorof case 205. A door 202 may comprise any suitable mechanism for openingand closing the case, and may be positioned in any suitable location. Asan example, a door 202 could be built into one of the sides of case 205,or a side of case 205 could itself operate as a door 202 (e.g., a hingecould attach one side of case 205 to another side of case 205). Incertain embodiments, door 202 may allow a portion of case 205 to bedetached and reattached to case 205. As an example, a top portion andbottom portion of case 205 could be latched together when case 205 isclosed and unlatched/separated when case 205 is open.

Case 205 may further comprise environmental buffers 204. Examples ofenvironmental buffers 204 include thermal buffers (such as insulationlayers or thermal phase change tiles) and humidity buffers (such assilica gel tiles). Certain environmental buffers may be implementedusing one or more tiles positioned within case 205. In certainembodiments, the tiles snap onto an interior surface of case 205, suchas the interior of door 202. In addition, or in the alternative, certainembodiments position environmental buffers within case 205 by placingone or more environmental buffers on or within platform 110. As anexample, thermal phase change material may be encased within platform110. Encasing the thermal phase change material within platform 110 mayprotect the tiles from damage, shock, and leakage and may ensure thatthe tiles are sufficiently close to load 120 to buffer the temperaturesurrounding load 120.

An example of encasing thermal phase change material within platform 110includes placing one or more thermal phase change tiles between a firstpanel (e.g., a front-facing panel) and a second panel (e.g., aback-facing panel) of platform 110. In other words, platform 110 maycomprise thermal phase change material sandwiched between the firstpanel and the second panel. In certain embodiments, the first and secondpanels may comprise aluminum honeycomb panels that encase thermal phasechange tiles within an epoxy adhesive matrix.

In certain embodiments, each thermal phase change tile measuresapproximately 5½×5½×1 inches (14×14×2.5 centimeters) and weighsapproximately 300 grams (10.4 ounces). Within the temperature range of15 to 30 degrees Celsius, each tile contains 50 British Thermal Units(BTU) of reserve thermal mass. Assuming a rate of 200 BTU reserve per1.5 cubic meter of enclosed space in order to add or subtract 15 degreesFahrenheit, and an average enclosed space of 1.5 cubic meters for amedium sized case 205, four tiles could be embedded within voids createdbetween the front- and back-facing panels of platform 110. Thermal phasechange material may be obtained from Cryopak™ or other manufacturers.

Vibration-damping footing 210 may be coupled to the bottom side of case205. One or more vibration-damping footings 210 may be utilized tosuspend case 205 from directly contacting a floor below.Vibration-damping footing 210 may be coupled to any suitable section ofthe bottom side of case 205. As an example, FIG. 2 illustrates twovibration-damping footings 210 coupled to the bottom side of case 205.Vibration-damping footing 210 may be coupled to case 205 through brace140 such that mechanical continuity exists from vibration-dampingfooting 210 to platform 110. Mechanical continuity may optimize thedamping performance of the vibration-isolating case 200.Vibration-damping footing 210 may be tuned to dampen certain damagingfrequencies, such as frequencies less than 5 Hz. In this way,vibration-damping footing 210 may be operable to reduce thesefrequencies from transmitting vibrations to load 120 within case 205. Inone embodiment, the amount and type of vibration-damping footings 210are selected based on the contents of case 205. Vibration-dampingfooting 210 is further described with respect to FIGS. 5-6 below.

FIG. 2 further illustrates that platform 110 couples to a plurality ofwire rope isolators 130. FIG. 2 includes four wire rope isolators 130toward the bottom interior region of case 205 that are illustrated aspositioned at an angle. To hold wire rope isolators 130 at an angle, oneor more support structures may be used. For example, FIG. 3 belowillustrates an example of a chevron-shaped support structure that canalso be used in the embodiment illustrated in FIG. 2. For purposes ofillustration, such support structure(s) are not expressly shown in FIG.2 in order to improve the visibility of other components in the figure.

FIG. 3 illustrates another example of vibration-isolating case 200, inaccordance with certain embodiments of the present disclosure. FIG. 3includes platform 110, shelf 115, isolators 130, brace 140, case 205,and vibration-damping footing 210 similar to those described above withrespect to FIGS. 1-2. The embodiment of brace 140 illustrated in FIG. 3provides an example alternative to the embodiment of brace 140illustrated in FIGS. 1-2. In FIGS. 1-2, brace 140 comprises individualrigid plates that mount to case 205. By contrast, FIG. 3 illustratesbrace 140 as a continuous frame that extends around a perimeter withincase 205. Brace 140 optionally includes one or more rigid plates coupledbetween the frame portion and isolators 130. For example, FIG. 3illustrates an example in which two rigid plates connect to the frameportion at an angle to form a chevron shaped support structure forisolators 130. The chevron structure may allow isolators 130 facingopposite sides of platform 110 to stabilize platform 110. Thus, platform110 may generally float between isolators 130 configured within thechevron structure, which can reduce the extent to which movement of case205 impacts load 120. Optionally, similar chevron shaped supportstructures could be used to support top isolators (e.g., 130 a, 130 b),bottom isolators (e.g., 130 c, 130 d), and/or side isolators (e.g., 130e, 130 f). In certain embodiments, the chevron shaped support structureis used only for bottom isolators (e.g., 130 c, 130 d) to provideadditional support in the load-bearing direction. In certainembodiments, the chevron shaped support structure is not used at all.

FIG. 3 further illustrates a crumple zone 142. FIG. 3 illustratescrumple zone 142 as generally located below platform 110. However,crumple zone 142 may refer to any area within case 205 likely toexperience a relatively high amount of shock, for example, in the eventthat case 205 is dropped. Suppose case 205 drops one or two meters. Theresulting impact may be on the order of 300 G at all frequencies.Crumple zone 142 can be configured with one or more shock absorbingstructures to absorb much of the impact and prevent damage to the objectin transit.

In certain embodiments, the shock absorbing structures may compressquickly in the event of a shock (such as a drop) and expand slowly afterthe shock to reduce rebound movement of platform 110. In addition, or inthe alternative, crumple zone 142 may include shock absorbing structuresthat compress quickly in the event of a shock (such as a drop) but donot decompress. Using a material that does not decompress may avoidrebound movement. If the structure in crumple zone 142 remainscompressed, it can be used as an indicator to identify whether case 205was handled improperly. This information can be used in making aninsurance claim for mishandling in transit. Examples of shock absorbingstructures include replaceable honeycomb, fluted, and/or corrugatedshaped structures composed of paper, polypropylene, polycarbonate,polystyrene (e.g., closed cell expanded polystyrene (XPS) core), and/orany suitable combination of the preceding. The selection of shape(s) andmaterial(s) of the shock absorbing structures depends upon the weight ofthe payload and the shock impulse to be absorbed. In certainembodiments, an inexpensive paper honeycomb material may be used as afirst, easily replaced shock-absorbing structure, and the paperhoneycomb material may be underlaid with a more expensive butgreater-energy absorbing plastic honeycomb or polystyrene structure andsmart foam to absorb shock from a catastrophic impact. In certainembodiments, shock absorbing structures of crumple zone 142 may beplaced within isolators 130. For example, as further described belowwith respect to FIG. 4, wire rope isolators can include a plurality ofloops 132. Shock absorbing structures may optionally be placed withinloops 132 to protect isolators 130 in the event of a shock.

FIG. 3 also illustrates an example of a latch channel 144 and latch 146.Latch channel 144 provides a point of connection for latch 146 toconnect to platform 110. Latch 146 extends across load 120 to helpsecure load 120 onto platform 110. Any suitable latch may be used, suchas a metal bar or a fabric strap. In certain embodiments, a metal bar(such as an aluminum bar) may be preferable to a fabric strap because afabric strap may tend to amplify vibrations in damaging frequencyranges.

FIGS. 4A-4B illustrate examples of wire rope isolators 130 forsuspension system 100, in accordance with certain embodiments of thepresent disclosure. Each wire rope isolator 130 may comprise a coil-likestructure having a plurality of loops 132 held together by one or morebrackets 134. As an example, each wire rope isolator 130 may include afirst bracket 134 operable to attach to platform 110 and a secondbracket 134 operable to attach to brace 140 of suspension system 100.Wire rope isolator 130 may further comprise a loop spacing 135 (e.g.,due to spreading that creates space between loops 132), a loop diameter136, and a wire thickness 137 (e.g., the diameter of the wire used toform loops 132). Each wire rope isolator 130 may act as a non-linearspring (i.e., the resistance of the wire rope isolator 130 increases asthe force upon it increases).

In certain embodiments, suspension system 100 may be madeself-centering. For example, wire rope isolators 130 (such as thoseillustrated in FIG. 4A and/or FIG. 4B) can be configured to minimize theextent to which platform 110 carrying load 120 moves from its initialposition in response to vibration and/or shock. The initial position canbe referred to as point (0, 0, 0) relative to the x-axis, y-axis, andz-axis. Return of platform 110 to the initial position (0, 0, 0) afteran excursion relative to the exterior shell can be optimized byarranging wire rope isolators 130 to oppose one another. For example,assume that a first wire rope isolator (“WRI-1”) opposes a second wirerope isolator (“WRI-2”). A movement that pushes WRI-1 would pull theopposing WRI-2 such that when WRI-1 undergoes compression, the opposingWRI-2 undergoes tension, and vice versa. Thus, opposing wire ropeisolators 130 keep the net effect of the movement as close to neutral aspossible.

In the example illustrated in FIG. 1, returning platform 110 to itsinitial point relative to the y-axis is accomplished at least in part byconfiguring wire rope isolator(s) 130 a at the top of platform 110 inopposition to wire rope isolator(s) 130 c at the bottom of platform 110and by configuring wire rope isolator(s) 130 b at the top of platform110 in opposition to wire rope isolator(s) 130 d at the bottom ofplatform. The opposing wire rope isolator(s) 130 may be aligned in thedirection of the y-axis. For example, left-top wire rope isolators 130 amay be aligned directly above left-bottom wire rope isolators 130 c onthe opposite side of platform 110, and right-top wire rope isolators 130b may be aligned directly above right-bottom wire rope isolators 130 don the opposite side of platform 110. In addition, the wire ropeisolators 130 may be aligned with vibration-damping footing 210 in thedirection of the y-axis. For example, wire rope isolators 130 c may bealigned directly above the left vibration damping-footing 210 and wirerope isolators 130 d may be aligned directly above the rightvibration-damping footing 210. Alignment in the direction of the y-axisincreases the damping effect of suspension system 100.

Returning platform 110 to its initial point relative to the x-axis canbe accomplished at least in part by configuring wire rope isolator(s)130 e at the left of platform 110 in opposition to wire rope isolator(s)130 f at the right of platform 110. In addition, the pairs of wire ropeisolators 130 at the top and/or bottom of platform 110 can be wound toreduce movement in the direction of the x-axis. As an example, a pair ofwire rope isolators 130 c may be configured at the bottom-left ofplatform 110. The first wire rope isolator 130 c(1) and the second wirerope isolator 130 c(2) can be angled toward each other to create somedegree of opposition in the x-direction. For example, wire ropeisolators 130 c(1) and 130 c(2) may be closer together at the pointswhere they contact platform 110 and may splay outward so that they arefurther apart at the points where they contact brace 140. Similarly, theother pairs of wire rope isolators (e.g., pair 130 a, pair 130 b, andpair 130 d) can each be wound to reduce movement in the direction of thex-axis. In certain embodiments, wire rope isolators 130 in a pair may beconfigured at a 120 degree angle relative to one another.

Returning platform 110 to its initial point relative to the z-axis isaccomplished at least in part by configuring wire rope isolators 130facing the front of platform 110 in opposition to wire rope isolators130 facing the back of platform 110. As discussed above, wire ropeisolators 130 may be configured in pairs, such as the pair of isolators130 c(1) and 130 c(2). Isolator 130 c(1) can face the front of platform110, and isolator 130 c(2) can face the back of platform 110.

Suspension system 100 may be configured such that each wire ropeisolator 130 is in a state of slight compression when platform 110 is inits initial position (0, 0, 0). Thus, suspension system 100 can respondto movements that cause one wire rope isolator 130 to undergo increasedcompression without immediately causing the opposing wire rope isolator130 to undergo tension such that the net movement of platform 110 isgradual and kept to a minimum.

Wire rope isolators can be tuned to accommodate both the load 120 andthe natural frequency of the load 120, thus achieving critical dampingof transportation-induced vibrations. Tuning can include selecting loopspacing 135, loop diameter 136, wire thickness 137, number of wires in arope braid, number of loops, number of isolators 130, angle oforientation of isolators 130 relative to platform 110, position ofisolators 130 relative to platform 110, and so on. As an example, as theweight of load 120 increases, wire thickness 137 can be increased, loopdiameter 136 can be decreased, and/or the number of loops can beincreased. In certain embodiments, wire rope isolators 130 are tuned toyield a tuning ratio greater than or equal to 1.4. The tuning ratio isdetermined by dividing a natural frequency of an object that thevibration-isolating system protects by a natural frequency of thevibration-isolating system. In certain embodiments, wire rope isolators130 can be tuned to isolate one or more frequencies in the range ofapproximately 8-50 Hz, depending on the object that thevibration-isolation system protects.

In certain embodiments, wire rope isolators 130 may be tuned separatelydepending on their position within suspension system 100. Wire ropeisolators 130 positioned proximate the bottom side of platform 110 (thegravitational load-bearing side of platform 110) tend to experienceheavier loading and may therefore be tuned to support more weight thanwire rope isolators 130 positioned proximate the top side, right side,and/or left side of platform 110. Thus, rope isolators 130 positionedproximate the bottom side of platform 110 can be tuned to support moreweight. As an example, wire rope isolator(s) 130 positioned proximatethe bottom side of platform 110 can have a different wire thickness,number of wires in a rope braid, number of loops in the wire ropeisolator, and/or loop diameter than wire rope isolator(s) 130 positionedproximate the top side of platform 110. As another example, wire ropeisolators 130 a and 130 b at the top of platform 110 can be tuned toprovide more flexibility and wire rope isolators 130 c and 130 d may betuned to provide more rigidity. This may allow platform 110 to providean inverted-pendulum movement such that the gravitational load-bearingside at the bottom of platform 110 stays relatively steady relative tothe top of platform 110.

In certain embodiments, a foam structure can be positioned through aspace formed by loops 132 of wire rope isolator 130 (e.g., the foamstructure can be placed through the space at the core of wire ropeisolator 130). The foam structure is operable to act as a safety stop toprovide impact attenuation and prevent wire rope isolator 130 fromcrimping or creasing in the event of a drop or similar impact. Forexample, FIGS. 4A-4B each illustrate embodiments in which wire ropeisolator 130 includes two brackets 134. The foam structure can bepositioned between the first bracket 134 and the second bracket 134 toprevent the first bracket 134 from coming into contact with the secondbracket 134 in the event of a drop or similar impact. The foam structuremay be made of material that is soft and cushy in low-impulseenvironments (e.g., impulses due to vibrations) and that stiffens inhigh-impulse environments (e.g., impulse due to dropping case 205). Forexample, the foam structure may comprise an impact-responsive, variablestiffness foam such as smartfoam, urethane foam (for example PoronXRDurethane), or other material that can compress rapidly and form chemicalcrosslinks that stiffen and absorb energy in high-impulse environments.The foam structure may have any suitable shape, such as a block shape, acylindrical shape, or, more generally, a mass of foam. In certainembodiments, the width/diameter of the foam structure is approximatelyhalf of loop diameter 136. This may allow some air space for wire ropeisolator 130 to flex in low-impulse environments without engaging thefoam structure. In certain embodiments, each wire rope isolator (e.g.,isolators 130 a-130 f of suspension system 100) can be configured with afoam structure as a safety stop.

FIG. 5 illustrates an example of a vibration-damping footing 210, inaccordance with certain embodiments of the present disclosure.Vibration-damping footing 210 comprises a mounting plate 220, a dampingsystem 230, and at least one cushion 240. In the example illustrated inFIG. 5, damping system 230 and cushion 240 are coupled directly tomounting plate 220. In alternate embodiments, damping system 230 andcushion 240 may couple to one or more other components which couple tothe mounting plate 220.

Mounting plate 220 may be made from aluminum or other metal, plastic, orany other suitable material. Mounting plate 220 may be custom or may bea universal design suitable for a variety of different applications. Thedimensions and material of mounting plate 220 may be selected based onthe size of case 205, the load 120, and/or other suitable factors.Mounting plate 220 may comprise one or more side portions 221 and/orflat surface 222. Flat surface 222 may comprise a top side (which may beconfigured to face case 205) and a bottom side (which may be configuredto face cushion 240). In the example illustrated in FIG. 5, mountingplate 220 comprises two side portions 221 extending away from flatsurface 222 such that mounting plate 220 has a channel-shaped structure.

To configure vibration-isolating case 200 with vibration-damping footing210, case 205 may be coupled directly or indirectly to vibration-dampingfooting 210. An example of directly coupling case 205 comprisesfastening mounting plate 220 to case 205 itself (e.g., using a bolt orscrew). An example of indirectly coupling case 205 comprises fasteningmounting plate 220 outside case 205 to a brace 140 inside case 205(e.g., using a bolt or screw that extends through a hole in case 205).For example, flat surface 222 may be positioned proximate a bottom outersurface of case 205 with the channel-shaped structure facing away fromcase 205, and flat surface 222 couples to at least one brace 140 withincase 205 (i.e., at least one brace positioned proximate a bottom innersurface of case 205). Thus, mechanical continuity may be provided fromvibration-damping footing 210 to suspension system 100 via braces 140.Mounting plate 220 may be oriented relative to case 205 such that itextends in the front-to-back direction.

In the example shown in FIG. 5, side portions 221 of mounting plate 220protect cushion 240 from damage. For example, movers may causevibration-isolating case 200 to slide laterally across the floor in theprocess of moving it. Such movement can cause a shearing force to beapplied to cushion 240. Side portion 221 may be operable to abut one ormore sides of cushion 240 and reduce damage from such shearing force.Side portion 221 may provide further protection for cushion 240 frompuncture or other damage. In certain embodiments, side portion 221 ofmounting plate 220 extends such that it abuts or covers a top portion ofcushion 240 and allows a bottom portion of cushion 240 to protrude, forexample, to allow room for cushion 240 to compress and expand inresponse to an impact.

Damping system 230 may be any system suitable to dampen vibrationstransmitting through the vibration-damping footing 210. In certainembodiments, damping system 230 may also lower the center of gravity ofvibration-isolating case 200. Lowering the center of gravity may improvestability of vibration-isolating case 200 and reduce movement of load120 within. In one embodiment, damping system 230 comprises a solidweight. In an alternate embodiment, damping system 230 comprises adamping material and a tray operable to contain the damping material. Inthe example illustrated in FIG. 5, damping system 230 comprises aU-shaped tray having a depth D and operable to contain a dampingmaterial. In the example, the tray is mounted to the bottom side of theflat surface 222, and the damping material is contained by side portions221. In an alternate embodiment, damping system 230 comprises a boxoperable to contain a damping material. The size, composition, mass, andother aspects of damping system 230 may be selected to optimize thedamping performance of the vibration-damping footing 210. An embodimentof damping system 230 is further described with respect to FIG. 6 below.

Cushion 240 may be any cushion suitable to suspend the mounting plate220 and the damping system 230 above a floor below. Cushion 240 may be acommercial product such as a Pelican SKID-MATE™. Alternatively, cushion240 may be a custom product manufactured based on the size of case 205,the load 120, or other suitable factors. The size, thickness,composition material, and other aspects of cushion 240 may be selectedto optimize the damping performance of the vibration-damping footing210. In the example illustrated in FIG. 5, cushion 240 is a donut-shapedpolyethylene bladder with an air-release hole 241 of diameter d_(h). Inthe example, cushion 240 may compress rapidly under a large shock byreleasing air through air release hole 241. The diameter d_(h) of airrelease hole 241 may be selected to restrict the speed that air mayreenter the polyethylene bladder to optimize the damping performance ofthe vibration-damping footing 210. Thus, in the example, cushion 240acts like a non-linear spring such that cushion 240 allows air to go outin response to an impact thereby causing air cushion 240 to compress andafter the impact allows air to go in more slowly than it went outthereby causing air cushion 240 to decompress slowly and avoid jostlingload 120.

In the example illustrated in FIG. 5, two cushions 240 are coupled tothe bottom side of flat surface 222 of the mounting plate 220. Withreference to FIGS. 1-2, vibration-isolating case 200 can be configuredwith the first air cushion 240 and second air cushion 240 positionedwithin the channel-shaped structure formed by mounting plate 220 suchthat the first cushion 240 is located toward the front of case 205 andthe second cushion 240 is located toward the back of case 205. FIGS. 1-2also illustrate an example having two vibration-damping footings 210: afirst vibration-damping footing 210 (e.g., located at the bottom side ofcase 205 and toward the left) and a second vibration-damping footing 210(e.g., located at the bottom side of case 205 and toward the right).

FIG. 6 illustrates an example of a vibration-damping footing 210, inaccordance with certain embodiments of the present disclosure. In FIG.6, part of side portion 221 is invisible to reveal damping system 230positioned between a first air cushion 240 and a second air cushion 240of vibration-damping footing 210. Damping system 230 comprises a tray231 operable to contain a quantity of inelastic particulates 232 and atray filler 233. Tray 231 may be made from metal, plastic, or any othersuitable material. Tray 231 may be custom or may be a universal designsuitable for a variety of different applications. In the exampleillustrated in FIG. 6, tray 231 is U-shaped and has a depth D selectedto optimize the damping performance of the vibration-damping footing210.

Tray 231 contains a quantity of inelastic particulates 232. Inelasticparticulates 232 may refer to any particulates that dissipate, ratherthan conserve, kinetic energy in response to a collision. For example,inelastic particulates 232 may vibrate against one another to dissipateenergy through inelastic collisions. Inelastic particulate 232 maycomprise lead shot or any other particulate suitable to dampen thevibrations of vibration-damping footing 210. In one embodiment, thedepth of the tray and the amount of inelastic particulate 232 (e.g.,lead shot) is configured to dampen frequencies less than 10 Hz. Forexample, the damping effects of inelastic particulates 232 may beconfigured to dampen vibrations less than approximately 5 Hz, such asfrequencies between 2 and 5 Hz.

FIG. 6 illustrates an example of the vibration damping characteristicsof inelastic particulates 232. In the example, vibration-damping footing210 experiences a vertical vibration in the positive y-axis direction,and inelastic particulates 232 absorb a portion of the resulting kineticenergy. This energy absorption may cause some inelastic particulates 232to become airborne. In the example, vibration-damping footing 210experiences a second vertical vibration in the negative y-axis directionand the airborne inelastic particulates 232 absorb a portion of theresulting kinetic energy when they collide with mounting plate 220. Inthis example, the inelastic particulates 232 may be operable to dampenvibrations which result from positive and negative movement in they-axis.

The ability to dampen vibrations from positive and negative movement inthe y-axis may be useful when transporting an object by truck, forexample. Typically, the truck bed continually goes up and down as ithits potholes or bumps in the road. The up and down motion can besignificant. Some of that is cushioned by the row of tires, however, thetruck's suspension system causes the tires to come back up very quicklyafter hitting a bump in the road. Inelastic particulates 232 can helpabsorb kinetic energy when the truck tires come back up. When the trucktires go down, inelastic particulates 232 sitting at the bottom of tray231 lift and absorb some of that vertical energy. When the truck tirescome back up, some of the inelastic particulates 232 that were liftedwill be falling and, when the inelastic particulates 232 hit the bottomof tray 231, will absorb some of the kinetic energy from the reboundmotion of the truck.

In certain embodiments, the depth D of tray 231 may be selected tocontrol the frequency of collisions between the inelastic particulates232 and the mounting plate 220 in order to optimize the dampingperformance of the vibration-damping footing 210. In certainembodiments, the quantity of inelastic particulates 232 and the diameterd_(p) of each inelastic particulate 232 may be selected to optimize thedamping performance of the vibration-damping footing 210. As an example,in certain embodiments, the depth D of tray 231 may be in the range ofapproximately 0.5 to 3 inches, the quantity of inelastic particulates232 may be suspended in air or in a aqueous gel medium and may fillapproximately 20-50% of the compartment formed by tray 231, and/or theinelastic particulates 232 may comprise lead shot particulates having amean diameter d_(p) size in the range of approximately 1 to 5millimeters and include a mixture of sizes.

Tray filler 233 may comprise a liquid, gas, gel, or other material. Inone embodiment, tray filler 233 comprises air from the atmosphere. In analternate embodiment, tray filler 233 comprises a gel selectedspecifically to optimize the damping performance of thevibration-damping footing 210. Tray filler 233 may be operable torestrict the movement of inelastic particulate 232 as they move insidetray 231. The quantity, density, pressure, and other characteristics oftray filler 233 may be selected to optimize the damping performance ofthe vibration-damping footing 210.

FIG. 7 illustrates an example container assembly for a load 120, inaccordance with certain embodiments of the present disclosure. Ingeneral, FIG. 7 illustrates load 120 arranged using a panel system thatplaces a substantially flat object 300, such as a painting, betweenpanels on the front and back sides of the object. Substantially airtightair gaps (i.e., sealed air compartments) between object 300 and thepanels increase stiffness and reduce vibration movement across object300. In the example illustrated in FIG. 7, a three panel systemcomprises, in order, a back panel 310, object 300, front panel 301, andstiffener panel 302. Back panel 310 is positioned behind object 300 andoffset by a first sealed air compartment, front panel 301 is positionedin front of object 300 and offset by a second sealed air compartment,and stiffener panel 302 is positioned in front of front panel 301 andoffset by a third sealed air compartment. In an alternate embodiment,load 120 may be a two panel system, comprised of, in order, back panel310, object 300, and front panel 301, without stiffener panel 302.

Using panels that are relatively more stiff than object 300 and that areoffset by sealed air compartments may control vibrations across object300. For example, in the embodiment illustrated in FIG. 7, back panel310 imparts its rigidity onto object 300, stiffener panel 302 impartsits rigidity onto front panel 301, and front panel 301 further impartsits rigidity onto object 300. This result is based on principles of theUniversal Gas Law applied to flat planes within a control volume system.The gas trapped in any sealed air compartment acts to resist motion ofone panel due to the resistance in motion of the other panel andresulting compression of the trapped gas. The effect is to quiet themotion of a flexible panel with a more rigid panel and ultimately toreduce the load on the object during transit and handling. The size ofthe offset between the planes can be tuned in order to minimize themotion of the flexible panel while maintaining enough of an offset toprevent the planes from colliding during any remaining vibration. Forexample, in the ideal case of two perfectly flat planes, the stiffnessof a 0.125 inch air gap is exceedingly high. For a displacement of 0.001inches the restoring force between the two planes is approximately 17pounds per square foot, assuming sea level air pressures, roomtemperature, and normal levels of humidity. For small gaps, themechanical stiffness between two planes is higher than casualobservation would seem to indicate.

In certain embodiments, the panel system may be tuned to raise thenatural frequency of object 300. As an example, assume the naturalfrequency of the canvas is 7 Hz. Back panel 310 can be configured todouble the natural frequency of the canvas (from 7 Hz to 14 Hz in theexample). Front panel 301 can be configured to increase the naturalfrequency of the canvas-and-back panel configuration by about one-third(from 14 Hz to 21 Hz in the example). Stiffener panel 302 can beconfigured to double the natural frequency of the canvas-backpanel-and-front panel configuration (from 21 Hz to 42 Hz in theexample). Other embodiments may tune the natural frequency to anysuitable value. As an example, for an object 300 having a naturalfrequency in the range of 1 Hz to 20 Hz, the first sealed aircompartment could be dimensioned so as to increase the natural frequencyof object 300 by at least 20%, the second sealed air compartment couldbe dimensioned so as to increase the natural frequency of object 300 byat least 20%, and the third sealed air compartment could be dimensionedso as to increase the natural frequency of object 300 by at least 20%.Additionally, the combination of the first, second, and third sealed aircompartments could be configured to increase the natural frequency ofthe object to at least 40 Hz. In certain embodiments, the panel systemcan prevent high displacement excursions, such as excursions greaterthan 350 microns. This may prevent movement or sagging that can occurwhen a stretched canvas is tipped, knocked over, or placed in ahorizontal orientation.

The use of small-volume, static gas piston principals to impart the highnatural frequency and low excursion properties of the rigid panels tothe less rigid object 300 may allow for limiting undesirable excursionsand raising the natural frequency of object 300 without directmechanical contact between object 300 and the other panels. For example,in embodiments where object 300 comprises a painting, air pistonsprevent front panel 301, stiffener panel 302, and back panel 310 fromdirectly touching the face of the canvas.

FIG. 8 illustrates an example container assembly for a load 120, inaccordance with certain embodiments of the present disclosure. FIG. 8illustrates load 120 as including an object 300 configured within apanel system. Object 300 may be a painting, canvas, or otherthin-membrane artifact susceptible to vibration. Object 300 may bemounted on stretcher 303. Stretcher 303 may provide a support structure,such as a wooden frame, and the edges of object 300 (e.g., the canvas)wrap around the sides of stretcher 303. In certain embodiments, object300 may be affixed to stretcher 303 using nails. Stretcher 303 may alsoincorporate cross members for added rigidity. Object 300 (stretched onstretcher 303) may be mounted in a frame 304, such as a gallery frame orother art frame. Frame 304 may include a recessed edge or rabbet withinwhich object 300 may be mounted.

As further described below, load 120 includes a plurality of gaskets 306to seal components of load 120 in place. Any suitable gaskets 306 may beused, such as closed cell polyethylene gaskets. In certain embodiments,a gasket 306 may form an air gap between components sealed by the gasket306. As an example, a gasket 306 may be used to form an air gap betweentwo panels. As another example, a gasket 306 (gasket 306 b) may be usedto seal and/or form an air gap between object 300 and frame 304. Incertain embodiments, gaskets 306 may be selected to provide an air gapwith a depth in the range of 3-5 millimeters. Load 120 may be pressurefit to compress the various gaskets.

FIG. 8 illustrates an embodiment in which the panel system includes afront panel 301, an optional stiffener panel 302, and back panel 310. Incertain embodiments, front panel 301 comprises a transparent glazingsuch as acrylic or glass that is relatively more stiff than object 300.In certain embodiments, the front panel has a thickness in the range ofapproximately 3-5 millimeters. Gasket 306 a creates a sealed aircompartment between object 300 and front panel 301. In certainembodiments, gasket 306 a is a 3-5 millimeter closed cell polyethylenegasket positioned between object 300 and front panel 301. A spacer 307may be used to increase the depth of the air gap between object 300 andfront panel 301. The spacer 307 in combination with gasket 306 a keepthe front panel in close proximity to the face of the object to increasestiffness, but sufficiently offset to ensure there are not collisionsbetween front panel 301 and object 300 during transit and handling. Asan example, spacer 307 may comprise a polycarbonate material and mayhave a height in the range of approximately 1-5 millimeters, such as 3millimeters. Thus, in certain embodiments, gasket 306 a together withspacer 307 form an air gap between the surface of object 300 and frontpanel 301 having a depth in the range of approximately 4-10 millimeters,such as 6-8 millimeters. Front panel 301 may be sealed within the rabbetportion of frame 304 by another gasket (gasket 306 d).

Stiffener panel 302 is an optional panel that can be used to provideadditional rigidity to load 120. Stiffener panel 302 comprises anysuitable material, such as paper honeycomb board or an aluminumhoneycomb panel. To impart more stiffness to object 300, stiffener panel302 may be more rigid than front panel 301 (which as discussed above maybe an acrylic glazing in certain embodiments). Stiffener panel 302 sealsto front panel 301 using gasket 306 e. In certain embodiments, the gasgap between stiffener panel 302 and front panel 301 is smaller in depththan the gas gap between front panel 301 and object 300. Making thestiffener panel 302-to-front panel 301 gas gap smaller that the frontpanel 301-to-object 300 gas gap makes the stiffener panel 302-to-frontpanel 301 gas gap significantly more rigid in compression. Thus,stiffener panel 302 meaningfully reduces the vibration of the entiresystem by reducing deflection under load of front panel 301, therebyrelieving the strain on object 300. In certain embodiments, gasket 306 ecomprises a 3-5 millimeter closed cell polyethylene gasket operable toproduce a substantially airtight seal between stiffener panel 302 andfront panel 301. In certain embodiments, stiffener panel 302 is held inplace by a clamp, tape, straps, or a box surrounding the completeassembly of load 120.

Back panel 310 may be coupled to the reverse side of stretcher 303 andmay form a continuous seal along the reverse side of stretcher 303. Forexample, back panel 310 may comprise a backing frame 311 that couples toframe 304 via gasket 306 c, wherein gasket 306 c is operable to providea substantially airtight seal. In certain embodiments, gasket 306 c is a3-5 millimeter closed cell polyethylene gasket. One or more fasteners305 may be used to secure backing frame 311 to frame 304. Examples offasteners 305 include a screw, nail, bolt, adhesive, etc. Note thatgasket 306 c provides a gap between frame 304 and the backing frame 311portion of back panel 310. The gap between back panel 310 and object 300may be relatively large, for example approximately three-quarters of aninch, depending on the depth of stretcher 303 and/or the thickness ofback panel 310.

In certain embodiments, back panel 310 further comprises adecontamination layer 312, a humidity control layer 313, and a backboard 314. Decontamination layer 312 may be positioned behind stretcher303 and may be operable to scavenge volatile organic compounds (VOCs),such as acid or aldehyde, or other contaminants emitted by object 300.As an example, a paper board comprising clay and/or activated charcoal(e.g., zeolite clay and activated charcoal embedded paper boards) may beused in decontamination layer 312.

Humidity control layer 313 may be operable to stabilize humidity. Incertain embodiments, humidity control layer 313 comprises apolypropylene felt containing a silica gel. The silica gel isconditioned to maintain acceptable humidity within frame 304. A dustcover may be positioned between humidity control layer 313 and object300 to prevent silica dust from getting on object 300.

Back board 314 provides stiffness to back panel 310 such that back panelis relatively more stiff than object 300. Back board 314 may comprise asubstantially rigid foam board. In certain embodiments, back board 314comprises a foam core polystyrene board or other material which mayprovide thermal insulation to prevent rapid temperature fluctuations. Incertain embodiments, back board 314 may further comprise an aluminumlayer (e.g., a layer on or within the foam board) operable to stabilizehumidity. As an example, back board may comprise a commercial productsuch as MARVELSEAL®, an aluminized polyethylene film for vapor proofingand humidity control.

Thus, back panel 310 may provide microclimate control by configuring oneor more environmental buffers (e.g., humidity control layer 313 and/orback board 314) to provide humidity and/or thermal protection.Microclimate control may refer to environmental buffers within backpanel 310 or within the sealed compartment formed between back panel 310and object 300. Certain embodiments may also provide macroclimatecontrol by configuring additional environmental buffers within case 205.Examples of environmental buffers for macroclimate control includethermal phase change tiles and/or silica gel tiles that can attach to aninterior-facing wall or door of case 205 and/or can attach on or withinplatform 110.

An alternative embodiment of load 120 reduces the corner volume onstiffener panel 302, which increases stiffness still further, byreducing the amount of compressible gas in the third sealed aircompartment without increasing the likelihood of a collision betweenfront panel 301 and stiffener panel 301 during heavy shock loading ofthe whole system, such as might occur if load 120 was dropped. That is,reducing the corner volume of stiffener panel 302 in turn reduces thecorner volume of the third sealed air compartment between stiffenerpanel 302 and front panel 301, resulting in a lower volume ofcompressible gas in the third sealed air compartment that enhances thestiffening effect imparted on front panel 301 from stiffener panel 302.This enhanced stiffening occurs where the volume of trapped air isreduced while still maintaining the same surface area on the face offront panel 301. This may be achieved through methods such as producinga concave geometry on the surface of stiffener panel 302 that extendsinto the third sealed air compartment to occupy space and/or producing astiffener panel 302 having a non-uniform thickness. This geometry may bepossible through using additive techniques such as three-dimensionalprinting. This may further be achieved by using a non-rectangulargeometry for gasket 306 e, such as an oval shape, that would eliminatethe corners where the displacement of a vibrating panel would beminimal.

Although FIG. 8 illustrates one example arrangement of gaskets 306,other embodiments may use different arrangements of gaskets 306. As anexample, with larger air gaps between backing panel 310 and object 300or between front panel 301 and stiffener panel 302 on a relatively largecanvas (e.g., 2 meter×4 meter) the gas piston space may be broken intoseveral smaller gas piston spaces by using gasketing to divide one largespace into several smaller spaces, thus adding the rigidity of a smallerpanel.

The various components described with respect to FIGS. 1-8 may becombined to form a vibration isolation system. The vibration isolationsystem may use any suitable combination of components, such as isolators130, vibration-damping footing 210, panels (e.g., front panel 301, backpanel 310, and optionally stiffener panel 302), and/or other components.Examples of other components include one or more sensors that mayoptionally be mounted in or on case 205, load 120, and/or object 300.Sensors may monitor and record vibrations and shocks occurring duringtransit, pressurization conditions, environmental conditions, GPScoordinates, surveillance cameras, and/or other suitable information.Additional examples of other components include humidity buffers,thermal controls (e.g., insulation materials, heating and cooling units,etc.), or other components selected to maintain optimal environmentalconditions within case 205.

The combination of components may be selected and tuned based on theobject that the vibration isolation system protects. As an example, asystem for protecting a stretched canvas or similar object may includevibration-damping footing 210 tuned to protect the canvas fromfrequencies in the range of approximately 0-10 Hz, a panel system tunedto increase the natural frequency of the canvas to at least 40 Hz, andisolators 130 tuned to yield a tuning ratio greater than or equal to1.4.

The tuning ratio is determined by dividing a natural frequency of object300 that the vibration-isolating system protects by a natural frequencyof the vibration-isolating system (such as suspension system 100). Foran isolation system to work, the natural frequency of the thing to beisolated (e.g., object 300 within load 120) must be higher than thenatural frequency of the isolation system. Over most of the spectrum,the number at which amplification starts to change to isolation is aratio of 1.4, which is the square root of 2 approximated to the nearestone-tenth. If the natural frequency of the thing to be isolated dividedby the natural frequency of the isolation system is less than 1.4, thenamplification will occur. Thus, the tuning ratio for achieving true,critical damping over most of the spectrum may be expressed according tothe following formula:(F _(p) ÷F ₁)≥1.4

In the formula, the tuning ratio is expressed as (F_(p)÷F₁), where F_(p)refers to the natural frequency of the payload being protected by thevibration-isolating system (e.g., object 300), and F₁ refers to thenatural frequency of the vibration-isolating system. As an example,applying the formula to a scenario in which the natural frequency of thepayload being protected (Fp) equals 14 Hz, the natural frequency of thevibration-isolating system (F₁) would be less than or equal to 10 Hz inorder to yield a tuning ratio greater than or equal to 1.4.

As an example, a vibration isolation system may be tuned to protect apainting on a canvas. A canvas tends to have the lowest naturalfrequency and is the most flexible as compared to other art media, suchas glass, marble, or ceramic sculptures and artifacts. Thus, thevibration-isolating system can be built to be able to isolate the lowestfrequencies (the frequencies associated with canvasses) and can then betuned according to the natural frequency of the object being isolated(e.g., canvas, glass, marble, or ceramic, and so on).

For purposes of the example, assume the natural frequency of the canvasis 7 Hz. To achieve a tuning ratio greater than 1.4 for the canvas, wirerope isolators 130 would be tuned to a natural frequency less than orequal to 5 Hz (i.e., 7 Hz divided by 1.4). However, configuring a wirethickness 137, number of loops 132, loop diameter 136, loop spacing 135,number of wires in a rope braid, number of wire rope isolators 130,angle of orientation of wire rope isolators 130 relative to platform110, and/or position of wire rope isolators 130 relative to the platform110 to achieve a natural frequency of 5 Hz may be impractical. Forexample, tuning wire rope isolators 130 to a frequency as low as 5 Hzmay require a relatively large wire thickness 137 that can be difficultto form into a small loop and may thus have a large loop diameter 136.Wire rope isolators 130 with a wire thickness 137 and loop diameter 136large enough to isolate low frequencies may take up too much spacewithin case 205. To address this problem, the panel system describedwith respect to FIGS. 7-8 can be used to increase the natural frequencyof the canvas, which in turn increases the natural frequency to whichwire rope isolators 130 would be tuned.

Continuing with the example, back panel 310 can be configured to doublethe natural frequency of the canvas (from 7 Hz to 14 Hz in the example).To achieve a tuning ratio greater than 1.4 for the canvas-and-back panel310 configuration, wire rope isolators 130 would be tuned to a naturalfrequency less than or equal to 10 Hz (i.e., 14 Hz divided by 1.4). Thenatural frequency of the canvas can be further increased with theaddition of front panel 301. Front panel 301 can be configured toincrease the natural frequency of the canvas-and-back panel 301configuration by about one-third (from 14 Hz to 21 Hz in the example).To achieve a tuning ratio greater than 1.4 for the canvas-and-back panel310-and-front panel 301 configuration, wire rope isolators 130 would betuned to a natural frequency less than or equal to 15 Hz (i.e., 21 Hzdivided by 1.4). The natural frequency of the canvas can be furtherincreased with the addition of stiffener panel 302. Stiffener panel 302can be configured to double the natural frequency of the canvas-and-backpanel 301-and-front panel 302 configuration (from 21 Hz to 42 Hz in theexample). To achieve a tuning ratio greater than 1.4 for theconfiguration that includes the canvas, back panel 310, front panel 301,and stiffener panel 302, wire rope isolators 130 would be tuned to anatural frequency less than or equal to 30 Hz (i.e., 42 Hz divided by1.4). In certain embodiments, the panel system may be tuned to achieve anatural frequency in the range of approximately 40-70 Hz for object 300,and wire rope isolators may be tuned to a natural frequency less than orequal to 50 Hz (i.e., 70 Hz divided by 1.4), such as a natural frequencyless than or equal to approximately 28.6 Hz (i.e., 40 Hz divided by1.4).

Certain embodiments of the present disclosure may provide one or moretechnical advantages. Certain embodiments may protect an object fromdamage due to vibrations, displacement, impact, temperature, and/orhumidity. As discussed above, any suitable combination of the componentsdescribed herein can be used to provide the desired protections.

Vibration protection can be provided by a combination ofvibration-damping footing 210, suspension system 100 comprisingisolators 130, and/or the panel system. In certain embodiments,vibration-damping footing 210 can be tuned to protect a canvas fromfrequencies in the range of approximately 0-10 Hz, a panel system can betuned to increase the natural frequency of the canvas to at least 40 Hz,and isolators 130 can be tuned to yield a tuning ratio greater than orequal to 1.4.

Excursion protection can be provided by the panel system and/orvibration-damping footing 210. The panel system can impart stiffness tothe canvas that protects against excursions. In certain embodiments, thepanel system limits excursions at the most flexible point (the middle ofthe canvas) to a value that does not affect the adhesion or cohesion ofthe paint to the canvas. For example, panel system can be configured tolimit excursions greater than 350 microns. In certain embodiments, thestiffness imparted by the panel system can prevent sagging of the canvasin the event that the panel system is tilted and can reduce thelikelihood of the canvas coming into contact with its glazing, forexample, in the event that a person inadvertently presses on thestiffener panel. In certain embodiments, some excursion protection canalso be provided by vibration-damping footing tuned to dampen lowfrequency (e.g., 5 Hz) vibrations from the transport vehicle that wouldotherwise impinge high energy on the canvas and result in excursions.

Impact protection can be provided by suspension system 100 (e.g., wirerope isolators 130), shock absorbing structures of crumple zone 142,and/or case 205 (e.g., a case comprising plastic, polycarbonatehoneycomb, polypropylene honeycomb, or other material that deforms onimpact and absorbs some of the energy of the impact). In certainembodiments, impact protection components are configured to limit thetotal G force in an impact resulting from a drop of up to one meter. Forexample, impact protection components can be configured to reduce thetotal impact shock to below 20G. As discussed with respect to FIGS.4A-4B above, a foam structure, such as a mass of smartfoam, can bepositioned within a wire rope isolator 130 to act as a safety stop thatprevents wire rope isolator 130 from crimping or creasing in the eventof an impact.

Temperature protection can be provided by macroclimate controls withincase 205 and/or microclimate controls within back panel 310 of the panelsystem. As an example, the macroclimate control may use thermal phasechange materials (e.g., tiles encased within platform 110 and/or tilesthat snap in and out of case 205) to maintain an internal temperaturewithin case 205. For example, the temperature may be maintained at 22°C., plus or minus 4° C., given an exterior fluctuation of 22° C., plusor minus 10° C. In other words, for exterior temperatures in the rangeof 12° C. to 32° C., the temperature within case 205 may be maintainedin the range of 18° C. to 26° C.

Humidity protection can be provided by macroclimate controls within case205 and/or microclimate controls within back panel 310 of the panelsystem. As an example, the macroclimate control may use silica gel feltwithin case 205 to maintain humidity within the range of 40% to 60%humidity given an internal temperature in the range of 18° C. to 26° C.

As a more specific example of combining the various components disclosedherein, an embodiment for transporting a stretched canvas or similarobject comprises a case 205 (such a hard shell case similar to thosemanufactured by PELICAN™ or STORM CASE™) configured with thermal phasechange material, humidity control material, wire rope isolators 130, acrumple zone 142, and a panel system comprising front panel 301,stiffener panel 302, and back panel 310, wherein the back panel 310 isconfigured to provide microclimate control. The thermal phase changematerial provides lightweight insulation that absorbs and releasesthermal energy in order to avoid significant temperature fluctuationswithin case 205. In certain embodiments, the thermal phase changematerial is implemented using tiles (e.g., tiles encased within platform110 and/or tiles that snap in and out of case 205). The humidity controlmaterial can be implemented using silica gel tiles that can attachinside the doors of case 205. Wire rope isolators 130, such as thosediscussed with respect to FIGS. 1-4, isolate platform 110 and load 120from damaging vibration frequencies. For example, wire rope isolatorscan be tuned to yield a tuning ratio greater than or equal to 1.4, thetuning ratio determined by dividing a natural frequency of an objectthat the vibration-isolating system protects by a natural frequency ofthe vibration-isolating system. Crumple zone 142 comprises shockabsorbing structures, such as XPS core, polypropylene honeycombstructures, or other shock absorbing structures described with respectto FIG. 3 above, to absorb the impact from shock in the event case 205is dropped. The panel system stabilizes the canvas against highdisplacement excursions, such as excursions greater than 350 microns.For example, as discussed with respect to FIGS. 7-8, a stiffener panel302 in combination with front panel 301 and back panel 310 providesrigidity to load 120. The back panel 310 is further configured toprovide microclimate control. For example, back panel 310 comprises backboard 314 (e.g., insulating foam core board that can include a vaporbarrier, such as an aluminized polyethylene film) and/or humiditycontrol layer 313 (e.g., silica gel felt).

Certain embodiments may have all, some, or none of the above-identifiedadvantages. Other advantages will be apparent to persons of ordinaryskill in the art.

Modifications, additions, or omissions may be made to the systems andapparatuses described herein without departing from the scope of thedisclosure. The components of the systems and apparatuses may beintegrated or separated. Moreover, the operations of the systems andapparatuses may be performed by more, fewer, or other components.Modifications, additions, or omissions may be made to the methodsdescribed herein without departing from the scope of the disclosure. Themethods may include more, fewer, or other steps. Additionally, steps maybe performed in any suitable order.

Although this disclosure has been described in terms of certainembodiments, alterations and permutations of the embodiments will beapparent to those skilled in the art. Accordingly, the above descriptionof the embodiments does not constrain this disclosure. Other changes,substitutions, and alterations are possible without departing from thespirit and scope of this disclosure, as defined by the following claims.

The invention claimed is:
 1. An assembly, comprising: a resilient,plastic-composite walled case having front, back, left, right, top, andbottom sides; a first vibration-damping footing located at the bottomside of the case and toward the left; a second vibration-damping footinglocated at the bottom side of the case and toward the right; whereineach vibration-damping footing comprises: a mounting plate having a flatsurface and side surfaces extending from the flat surface to form achannel-shaped structure, the mounting plate coupled to the case suchthat the flat surface is positioned proximate a bottom outer surface ofthe case with the channel-shaped structure facing away from the case andextending in the front-to-back direction of the case, wherein the flatsurface couples to at least one brace within the case, the at least onebrace positioned proximate a bottom inner surface of the case; a firstcushion and a second cushion positioned within the channel-shapedstructure such that the first cushion is located toward the front of thecase, the second cushion is located toward the back of the case, and theside surfaces of the mounting plate protect at least a top portion ofeach cushion; and a damping system comprising a tray containing aquantity of inelastic particulate, the tray positioned between the firstcushion and the second cushion; and a platform mounted within the casesuch that a mechanical path exists between the platform, the at leastone brace, and the first and second vibration-damping footing.